Selectively controlled torque actuated clutch transmission mechanism



H. J. MURRAY Nov. 17, 1936.

SELECTIVELY COINTROLLED' TORQUE ACTUATED CLUTCH TRANSMISSION MECHANISM Filed April 8, 1955 2 Sheets-Sheet l Nov. 17, 1936. 'H J. MURRAY 2 Sheets-Sheet 2 Filed April 8, 1955 Patented Nov. 17, 1936 iTE S PATENT oFFicE NISM Howard J. Murray, New York, N. Y.

Application April 8, 1935, Serial No. 15,176

30 Claims. (Cl. 19248) My invention relates in general to a simple control device for positively eecting the actions of reversible unidirectional clutching elements selectively employed to effect the power transmitting relations of driving and driven power members.

'One of the general objects of my invention is to providecontrol elements by 'means of which reversible unidirectional clutching elements with an intermediate fully released position may be selectively actuated whereby a selected driving member may be connected to a driven member by virtue of power derived from the relative roy tation of the said driving and driven members. i5 Another object of my inventio-n is to provide a simple power actuated reversible unidirectional clutch control organization including a control responsive to a relatively light control force for causing the said control to begin to function and 20 additional means for causing the said organization to complete the clutch actuation by virtue of power derived from the relative rotation of certain associated power members.

Still another object of my invention is to pro- 25 vide selective control means designed to eiect the positive actuation of reversible unidirectional clutches to and from an operative position wherein the energy for said actuation is obtained from associated power members within the confines of 30 the transmission casing.

A further object of my invention is to provide a roller clutch organization wherein reversible unidirectional declutching action will be automatically eected by camming means actuated 4 35 by power previously derived from relative rotation of drivingand driven members.

.An additional object of my invention is to provide a reversible unidirectional clutch control means designed to positively actuate interlccked ro reversibie unidirectional clutches with'an intermediate fully released position into and out of clutching position with driving and driven members by Opposing the relative rotation of the power members to be clutched. 45 .A still additional object of .my invention is to provide a reversible unidirectional clutch organl ization in which the positive actuation of the clutches into and out of clutching position will be definitely and positively effected by power ob- 50 tained due to relative rotation vof driving and driven members therefrom to tend to cause the members to approach a common speed, and to thereafter impart relative motion between the members to effect declutching action.

55 A still further object of my invention is to prointo Patents 2,051,386 and 2,051,385, respectively.

The present disclosure provides means for positive declutching action by varying the speed of one of the members relative to the common driving speed by power derived from the members previous to the clutching relation. The declutching action therefore does not depend on the variation of the power supplied to the transmission. According to the present disclosure the positive actuation of the clutch-rollers into and out of a clutching position is accomplished by providing means arranged to obtain power by virtue of the relative rotation of the power members. In one embodiment ofthe present invention this power is obtained during the selective movement of the clutch-rollers toward a clutching position-thence automatically held in suppression during the normal driving relation of the power members, and finally released to effect the declutching action.

As the power for positive clutch actuation is derived from the inherent power represented by the relative rotation of the driving and driven members, it is obvious 'that the derivation of this 35 clutch actuating power tends to decrease proportionally the relative rotation of the driving and driven members and. thereby causes the said members to approach a common speed prior to a driving relation.

The present disclosure thus provides means for positively controlling the movement ci the rollers into clutching engagement Withthe driving and driven members so that the noise and shock usually accompanying clutch roller action in clutch devices as now known is eliminated.

it is obviousl that in order to positively effect declutching action of reversible unidirectional clutches under all conditions of operation that the declutching action will require power sufcient to rotate the clutched members relative to each other.

As this clutch actuating power is derived by virtue of the relative rotation of the driving and driven members during the movement of the clutch rollers towards a clutching position, it is obvious that the derivation of this power will act to bring the driving and driven members to a common speed. With proper design, it will be possible to bring the driving and driven members to a synchronous speed before the rollers move to a clutching position. Thus the driving and driven members are placed in driving relation by means energized by power derived from the relative rotation of the said members.

In the following description names will be given to parts for convenience of expression, but the names are intended to be as generic in their application to similar parts as the art Will permit.

The invention allows numerous physical embodiments and a preferred type is herein illustrated for the purpose of showing an application of the invention, but it is hereby understood that the showings Ain the drawings are largely diagrammatic merely being 'sufficient in, detail to show `applications of the invention. l

'In the drawings: *Y

Figure l is a fragmentary View of part of a power transmission equipped with a selective control organization, and a torque actuated reversible unidirectional clutch means having inventive features as disclosed in this application.

Figure 2 is a transverse sectional view taken along the line 2-2 of Figure l in the direction as indicated by the arrows.

Figure 3 is a transverse sectional view takenv along the line 3-3 of Figure 1in the direction as indicated by the arrows.

Figure 4 is a transverse sectional view taken along the line 4 4 of Figure 1I in the direction as indicated by the arrows.

Figure 5 is a transverse sectional View taken along the line 5-5 of Figure 1 in the direction as indicated by the arrows.

Figure 6 is a sectional view showing five positions of the interlocked cams and indicates the means for preventing the simultaneous actuation of both setsof clutch rollers.

Figure 7 is a sectional view invelevation showing a modification of the axially slidable selective control means shown in Figure 1 so as to provide a slip-clutch' or give-away connection.

Figure l8 is a View in sectional elevation indieating a modification of the selective control means of Figure 41 whereby unidirectional actuation of the clutch rollers is effected in one direction as indicated by the arrows.

y The present disclosures relates to a selective speed power transmission mechanism including driving and driven members in whichI have brought toge'therin a simple manner in, combination with positively controlled reversible unidirectional Vclutches with an intermediate fully released position, a selective control means, a self-energized actuating means for positively and definitely moving the said reversiblel unidirectional clutches to and from operating positi'ons'for quietly effecting vdesired speed relations between ythe driving and driven members through the agency of the said clutches, Said selective control and said self-energizedactuating means. Referring to the drawings, there is shown in Figur'l a normally driving power shaft 4 conriefitedv to a suitable source ofV power supply, such as an internal combustion engine as commonly found on automotive vehicles. (not shown).

' Ayr'sh'aft 6 hereinafter designated as the normally driven member of the transmission is connected to drive the wheels of the said vehicle.`

The shafts 4 and 6 preferably are positioned iti axial alignment by means of the bearings 9 suitably positioned in a recess in the shaft AIl.

For the purpose ,of this description, the means shown by Figure 1 may be considered as a fragmentary portion of a selective. form of speed v' ciated parts as well as the means for connecting the shift rods to same are not shown. According to the present invention it is intended to use any known selective actuating means to move the shift rods (not shown).

In general it may be assumed that the means shown in Figure 1 are primarily for the purpose of selectively placing the transmission in a socalled direct or second speed status. The gear 39 is shown constantlyin mesh with the engine gear'5, and the gear 36 is indicated as being constantly in mesh with the loosely mounted power gear 34, and the gears36 and 39 are assumed to be portions of a counter-shaft cluster (not shown).

The normally driven shaft t isassumed to be connected to a conventional propeller shaft through a conventional universal Ajoint and is formed with an enlarged portion 'I provided with a plurality of clutching surfaces I4 as shown by Figures 2, 3, 4 and 5.

The clutching .surfaces I4 in the present disl closure are formed by grinding away 6 sections of a round shaft so as to form aplurality of surv faces symmetrical about the axis of the shaft 6, but it is obvious that the number and form of the surfaces may be varied to suit the conditions under which the device may be installed and y operated.

In any event the surfaces are intended to position two sets of reversible unidirectional clutchroller elements I9 and 24 housed Within the outlines of the flanged portion II of the engine gear 5 and the flanged portion I0 of the gear 34. The clutch-rollers I9 and 24 may be considered as consisting of a plurality of sets of reversible unidirectional rollers in the form of solid steel cylinders designed to selectively engage the inner driving surfaces of the projecting portions IIJ and II when moved relative to the radially varying surfaces of the enlarged portion 'I of the driven member 6 so that one may be driven from the other according. to the' operative status of the said rollers.

The clutch rollers 24 'are formed so that the projection I I of the engine gear 5 may selectively drive the power member 6 in a clock-wise direction, or the member 6 may drive the projection I I in a clock-wise direction as viewed from the left hand end of Fig. 1. In the same manner the set of rollers I9 will drive the member 6 from the projection I0 in a clock-wise direction, and the member IIJ from the member 6 in a clock-wise direction as viewed from the left hand end of Figure 1.

It should be noted that the projection II is integral with the engine gear 5, and that the projecting portion ID is formed integral with the loosely mounted gear 34. Thus the portion 5I will rotate at the speed of the engine shaft 4, and the portion I Il will rotate with the gear 34.

i All of the clutch rollers I9 and 24 forming the clutches are normally held in the intermediate aoeaacs fully released position shown by Figure 2 by cen--I tering springs i8 designed to normally hold the rollers symmetrically in the openings 2t formed between the actuating elements 22 provided with recesses 23 shaped to receive and position the springs i8. The actuators 22 are symmetrically positioned about the shaft portion to rotate on the curved portions 25, and are securely attached in a suitable manner to the end rings 2S and 2l to rotate therewith.

The actuators 22 and the end rings 26 and 21 are formed to move within the space between the shaft portion 1 and the projection il, and therollers I9 and associated end rings 29 and 3| are movable within the space formed between the shaft portion 'l and the projection lil.

The ring shaped members 2l and 29 are formed with servo-cam recesses to receive mating cam projections 2| and d8 (see Figure 6) formed on the axially slidable elements I3 and l5 fitted to the surfaces I4 so as to rotate at all times with the enlarged portion l. The driving projection II is formed with an opening to receive and restrain for radial movementa control member l5 indicated by the steel ball I6 of Figure 3. 'Ihese balls I6 are positioned in the path of the cammed surface 32 formed on the left hand end of the axially slidable control member 33 arranged to receive a shift finger 3|] in the slot 35 between the nanges 8.

Variable radius slot-s 33 and t1 formed in the actuating ring 2l are positioned directly beneath the balls IG and in their path of movement. Similar balls il are positioned in the projection l0, and similar variable radius slots are formed in the actuating ring member 2t. The elements i3 and l5 are formed With splines 4o and di to t mating splines 8 shaped on the axially slidable member 33 so that the members i3, I5 and 33 may move relative to each other axially as they rotate with the shaft portion l. A ilanged projection te is formed on the element I3 so as to provide a wide bearing on' the surfaces M.

A similar flanged projection is formed on the axially slidable member I5. This projection 86 (see Figure 6) is spaced axially from the projection lil to provide a neutral nonf-operatinglaxial' clearance de. The cams 2| projecting from the member I3 are shaped with cam faces t2 and G3 designed with a desired included angle. The cams 2| of the member i3 are assumed to be rotated about the axis of the shaft portion 1 through an angle of 60 degrees relative to the cams d8 of the member i5.

A coiled spring I2 (see Figures 1 and 5) is positioned between the axially slidable members i3 and l5 and coiled about the portion I of the shaft 6. The spring is supported on the flanged extensions ill and itt.' As the spring is extended the members are axially xed by the split rings 5l) so positioned on the portion l as to permit the installation and removal of the members I3 and i5 when the spring I2 is properly compressed.

Figure 6 includes 5 sectional sketches riesignated as A, B, C, D and E showing the action of the clutch roller interlocking means as well as the relations of the cams 2| and d8. Sketch A indicates the relative position of the parts with the shift fork 39 in the position shown by Figure 1. Sketch B indicates the position of the cams and associated parts as the projection Il drives the portion 1. Sketch C indicates the position of the parts as the member 1 drives the portion Il It should be noted that the space 49 is now occupied by the ange portion M. This is also true for sketch B. Sketch D indicates the position of member 2l of Figure 3).

of the shift i'lnger 3i) is thereby transmitted tov the parts as' the projection it] drives the portion l, and sketch .indicates the positions as the portion l drives the projection EID.

The operation of the device is described as follows. y

If the vehicle upon which the transmission is installed is in motion, the power member 6 is thus rotated by the rear wheels, and thereby the shaft portion l and the elements of Figure 1 including the rollers it and 2t, cammed members 2l, 29, i3 and I5, spring I 2, and axially slidable member 33 will rotate with the shaft 6. If the vehicle is at rest the shaft ii and the parts arranged to rotate with it are at rest.

If the engine of the vehicle is running the conventional clutch (not shown) may be employed to rotate the engine shaft Il and the associated parts including the gear train 5, 39, 36 and 34 and thereby the hub extensions il) and Il and also the control balls it and i'' carried thereby. I

If either the engine or vehicle (or both) are in motion the hub extensions I0 and El and the roller sets i9 and 26 may relatively rotate about the common axis of the shaft portion Let it now be assumed that the vehicle or engine (or both) are moving and that the operator of the driving projection il! forming an integral portion of the intermediate driving gear 3d connected by gear train including jack-shaft gears 36 and 3Q to the driving shaft 4. Continued axial movement oi the member 33 to the right results in an over-=riding action of the camming surface of the end portion 5i) to radially depress the control balls il downward along their openings in the portion il).

.The roller actuatingand cammed member 29 shown directly in the path of the balls Il is provided With' one or more cammed tracks 38 and il (similar to the cammed tracks 38 and 4l of The axial movement the balls I7 to hold them radially inward so that the relative movement of the members li) and 2i) will cauce a clutching engagement between the balls Il and the member 29 due to the reaction against the cammed tracks 38 and dl. Thus there is provided a force resolving organization whereby a relatively slight force initially applied to the sli-dable member 33 inaugurates a relatively large clutching force between the driving member and the driven member i5. But Athe cammed element 29 is connected to the resiliently held mating cammed member i5 mounted for rotation with the driven member 5 as it moves axially. Thus as the member 29 is clutched to the member ii! to tend to rotate with the driving member l the member i5 continues to rotate 'with the driven member t. The members 29 and I5 thus tend to rotate relative to each other, and because of the cammed connection due to the mating cams i3 a relative axial movement must accompany said relative rotary movement.

But any axial movement of the member l5 will be resisted by the spring l2 to the extent of its resisting' ability. It the axial resultant of the cam action between the members 29 and I5 is greater than the resistance of the member l2 the member I5 will be moved axially to the left thus V.the vehicle desires to place the transmission in permitting relative rotary movement vbetween the members I5 and 29 and thereby a relative movement between the members 4 and 6,l and also a relative movement between the rollers I9 and the shaft portion l of the shaft 6. With the rollers displaced from the position shown in Figure 1, itis evident that power has been stored Ain the spring I2.

The clutching action of the balls I'I and the cammed tracks 38 and 41 of the member 29 is progressive and is completed by the inherent power represented by the difference of speed of the members I0 and 29. It is evident that the resultant forces reacting to push the balls Il radially outward in turn produce an axial component force tending to move the axially slidable member 33 to the leit, but it is obvious that this axial force applied to the member 33 may be caused to bevery small compared to the reaction between the balls Il and the cammed surface of the portion 59 by proper design.

The gripping of the member 29 by the balls Il results in relative axial movement of the cammed member I5 and also causes relative rotary movement of the members I5 and 29 and thus the rollers I9 are also moved from the inoperative position shown in Figure 1 relative to the shaft portion l so as to rotate relatively clock-wise. As the camming action of the cams 48 between the members I5 and 29 continues the spring I2 is being compressed and the rollers I9 are being positively moved toward a positive clutching position between the power members I0 and 6. The power for causing this camming action and compressing the spring is derived from the relative rotation of the 'members I0 and 6, and thus the driving member 4 and the driven member 6. Power is thus transmitted between the driving and driven members 4 and 6 to cause the members 4 and 6 to approcah a common speed. If the spring I2 is properly designed this transfer of power may be accumulative and regenerative due to the reaction between the cam surfaces of the members I5 and 29. When the common resilient element I 2 is provided with suillcient resistance against compression, it is obvious that power may be transmitted between the members 4 and 6 before the clutch rollers I9 and 24 have been relatively moved into clutchmit the driving member to move the clutch rollersl into a positive drive clutching position.

Thus in normal operation for a selected speed,'

the members 4 and 6 would be in a resilientl drive relation, and would automatically move them- -selves into a positive drive relation during intervals of excessive torque relations.

Thus-the camming means of Figure 1 is torqueactuated when an initial axiall force is applied to the shiftable member 33, but the initial force 'does not have to be maintained tosustain the said state of torque-actuation. It is true that the shiftable member 33 has to be axially positioned to continue to depress the balls I1, but itsposition is maintained by the conventional interlock (not shown) and no axial force is necessary.

Now let it be assumed that the resistance spring I2 is provided so as to have sufficient resistance strength for the conditions under which the Vtransmission will be installed and operated. In any event the initial operation of the shift nger to the right will result in a transfer' of power from onemember (4 or 6) to the other and to the spring I2 to cause the members 4 and 6 to approach the same speed as vthe rollers I9 tend to move toward a clutching position `whereby one of the members may positively drive .the other power member (see members-4 and 6,

Figure l).

Thus the member I9 will be positively connected to the driven member 6 with suiicient relative movement of the rollers I9 to positively drive the member 6 in a clock-wise direction as viewed from the left hand endof Figure l. In the same manner the power member 6 will be connected to the rmember IIJ to drive the same in a clock-wise direction as viewed from the left hand end of Figure 1.

It should be noted that the change of driving relations between the members I0 and 6 is automatic as long as the axially shiitable member 33 is in an operative position as will be seen by reference to sketches A, B, C, D, and E of Figure 6. members 4 and when the axially slidable member 33 is ina neutral position and with the cammed surfaces ofthe members 2|, 2l, 29 and 48 fully seated.

Sketch D indicates the relations of the cammed members when the projection I 0 is driving the member portion l, and sketch E of Figure 6 indicates the position of the cammed members I5 and 29 when the-normally driven portion l is driving the projection I0.

Inactual operation of a vehicle the members 4 and 6 may either become the driving member and thus the direction of power transmission constantly changes. As the projection IIl drives lthe member 6 and then the member 6 drives the member I0, it is obvious that as the member E tends to rotate faster than the member I0 with the cams in the position asshown by sketch D of Figure 6 the necessary torque required to hold the cammed projections 48 in the position shown no longer exists and the energy stored up in the spring I2 will azt to positively move the rollers I9 to the position shown in Figure 2, and the cams to the position shown by sketch A of Figure 6. It should be noted at this time that the space 49 between the flanged projections 44 and 46 of Sketch A indicates the relations of thek the members I3 and I5 is approximately taken up as the member I5 is moved to the left as shown in sketch D. As the member 6 now exceeds the speed of the projection I0 the cams will be seated as in'sketch A and thence immediately moved to the position as shown by sketch- E. Thus the opening 49 will be closed,

again. As the cams move to and from the positions shown by sketches D and E the member I3 cannot be moved to the right during the clutching action pf the rollers I9 and the danger of simultaneous clutching o'f the sets of rollers: I9 and 24 is definitely and positively eliminated.`

Hence according to the present disclosure I provide air automatic interlock between thesaid Sets of reversible unidirectional rollers I9 and 24. Still further it should be noted that in the event of axial movement of .both members I3 75 and I toward each other, that the space 49 will be jointly occupied and the flanges 44 and 46 will intercept each other before either of the Y sets of rollers I9 and 24 may be moved to a clutching position with the power members.

This action of changing the driving and driven relationsv of the power members I0 and 6 is an automatic function of the torque relations of the members I0 and 6 and occurs Without any change of status of the control elements 39, 33 and I'I except the change in direction of the force resolutions between the balls II and the member 29. v

Conditions of operation can exist, however, wherein the member I0 is driven from the member Ii and it is desired to move the rollers I9 and thus the member 29 from a clutching position as shown by sketch E of Figure 6 to the neutral position shown by sketch A. With the conventional clutch (not shown) connected to the drlv ing'member 4 out it is obvious that the tendency of the lmember I0 is to decelerate and thus continue to be driven by the member 6 as long as member 6 has rotation. In this event it becomes necessary to provide for the declutching of the rollers I9 with the members IIJ and 6; But

the member I0 must beI placed in a state of tendency to rotate faster than the member 6 in order to free the rollers I9 or the rollers `I9 must be provided with a suiicient torque to positively move the rollers from the said clutching position. In order for the servo-cams of members I5 and 29 and thus the rollers I9 to be 'first moved to a clutching position it is first necessary to compress the spring member I2 from the position shown in sketch A'of Figure 6. The power acquired by the spring during compression remains stored up in the spring during the clutching action of the rollers,I9. This stored power is assumed for thev purpose of this description to be of sufficient magnitude to move the clutch rollers I9 fromV a clutching position (the conventional clutch remaining out) When the member I0 is connected to the engine of the vehicle with the'member '6 still remaining the driving member, it is obvious that the spring could not practically accelerate the member IIJ with respect to the speed of the member 5.

The approximate maintenance of speed of the member I I] under' the driving conditions indi.

of the member I0 cannot become less than the speed of the member 6. Thus the only requirement of the torque producing ability of the compressed spring I2 acting through the servo-cams 48 of the members YI5 and 29 is that the-spring impart an infinitesimal.acceleration or tendency to acceleration of the member I0 and/or be able to positively move the clutch rollers I9 from a clutching position.

The form of the spring I2 is immaterial, as well as its direction of movement. The only requirement is its ability to receive and store power from the power members, and then to return this power to aid in declutching the rollers I9 and 24. The spring I2 may be made so as to taper from the center to the ends so that the resistance will increase as it is compressed, and correspondingly. decrease as it expands. Still further the cams 2I may be so formedas to require greater forces while compressing the spring than is subsequently returnedby the spring to the members 21 and 29. It is obvious thatthe cam angles of the surfaces shown by Figure 4 may be varied to produce an unlimited series of combinations of axial and transverse components.

According to the present disclosure, the spring I2 may be relatively so strong as to always bring the driving member IIJ and the driven member 6 to a driving relation before the rollers E9 are moved into a clutching relation, or the roller clutches i9 and 24 will not be moved to a clutching position except during periods of excessive driving torque ,relations between the member 6 and the member I9 or Ii. In this event the rollers i9 would more or less float between av neutral position and a lclutching position as the members II! and 5 are moving together at approximately synchronous speed.

Normally as long as the 'conventional clutch between the engine (not shown) and the member I0 is held out", this iloating action will continue. If now this conventional clutch is let in the member I9 will acquire a comparatively great torque, and the rollers I9 will be moved to a clutching position; position of the rollers I9 and 24 will depend on the directional relative rotation of the members IIJ and 8,that is, whether the vehicle is to drive the engine, or the engine drive the vehicle. In either event sucient torque may now be obtained from the members Il) and/or B to operato the cams 2| against the spring I2 to compress it still farther from its initial compressed position to positively move the rollers I9 into a clutching l position, Such action willv start at the instant The actual clutchingA of change from a balanced resilient relation between the power members I0 and 6 and the rollers I9 will be moved to assume the clutching action without jar or shock. Of course, all degrees of synchronism are possible with proper design of cams and spring. The spring I2 may be only of sufficient strength to partially synchronize the members, before the rollers I9 are moved into clutching position. But, whatever the degree, the relative speed of the members I I) and 6 will be decreased to correspondingly decrease the j ar and shock of the clutching action of the rollers i9.

Now let it be assumed that the operator of the vehicle wishes to change the transmission from intermediate speed to direct drive. In this event the operator moves the shiftable element' 33 from the extreme right to the left, passing through .the neutral position shown in Figure 1. The inclined surface of the portion 59 moves also to the rleft releasing the control balls I'I from clutching relation with the cammed track portions of the member 29.

Whatever the position of the clutch lrollers I9 may be at this instant of freeing the control balls I'I, it is evident that the spring I2 will tend to return the clutch rollers to, or retard the clutch rollers I9 in, the position shown in Figure 2.

As the shiftable member 33 is moved to the left from neutral position the camming surface of the portion 32 will now move the control balls I6 radially inward to grip the balls with the cammed track vportions 38 and 4'I (see Figure 3) and thereby clutch the anged portion I I of the driving gear 5 with the cammed element 21. The portion I I now tends to drag the portion 21 with it as also does the cammed portion I3 in the same manner as hereinbefore described for the reactions of members I0, 29 and I5. .The cai` s 75 2| (see Figure 4) provided with the surfaces d2 and 43 will react with the camming surfaces of the portion 21 to cause axial movement of the member I3 to the right and at the same time a relative rotary movement of the rollers 24 (see Figure 2) with the shaft portion 1 according to the relative movement of the driving member I I and the driven member 6.

With a suiiiciently powerful spring I2v the power members II and 6 will be caused to approach the same speed before they are placed in positive drive relation, by the power derived from the relative clock-wise or counter clock-- wise movement of the members II and 6.

This rapid change may be made with a small l initial force/applied to the shift fork 30, and a return of the shiftable member 3l] is possible without reference to the instantaneous torque relations of the power members Il and 6.

Figure 1 indicates a form of torque synchro'- nizer in which driving and driven members I I and I 6, and IIl'and 6 are caused to assume the same speed through the agency of a resilient resisting member I2, the power for actuating the said member I2 being derived from the driving and the shift fork 30.

driven members to be synchronized. The power for overcoming the resisting member I2 is attained by causing either or both of the said'power members to transfer power from one to the other. In Figure 1 the cammed member 21 is placed into operative relation with the member II immediately upon the application lof the manual or other inaugurating force applied to axially move Under some circumstances, such as for instance, where the members I I and 6 are moving at high relative speed and when one or both members and 6 are turning with strong torque forces, the rotating cams 2l and-thus the members 21 and I3 will tend to impose a strain on the parts not necessary to the proper synchronization of the driving and driven members. Accordingly there is indicated by Figure 7 a modified form of control which retains all of the advantages inherent in the structure included in the means of Figure 1, and which at the same time provides for some exibility in the camming engagement. It is obvious vthat the greater the relative torque force between the driving and driven members the greater is the amount of work or transfer of power necessary to overcome this power and to deprive the driving and driven members of their relative speed. The modification as indicated by Figure 7 provides give-away means 5I and 54 in the form of annular springs secured to the axially slidablememberl 33 by means of fasteners 52 and 53. With the member 33 moved to the extreme left the spring 5I maintains the balls I6 capable of engagement with the cammed member 21, but at the sa'me time permits the balls I6 to automatically and intermittently move to an operative position with respect to the cammed tracks. 38 and 41 (see Figure 3) of the cammed member 21 until a period of time has elapsed suicient to decrease the relative speeds of the member II and member 1 thereby to permit complete and continuous operation of the cams of the members I3 and 21 to bring the normally driving member II and the driven member 1 to a common speed. The continuous operation of the balls starts as an automatic function of the torque relations 'of the driving member II and the driven member 1, and/or the resisting qualities of the give-away member 5I. Each intermittent clutching action of the balls I6 with the cammedmember 21 results in a transfer of power between the members I I and 1, and each transfer of power reduces the torque and thereby the relative speed of the said members.` When the relative speeds have been suiiiciently reduced due to a series of successive transfers of power the resisting member 5I will then be able to hold the balls I6 continuously in operative clutching position as described for the operation of the means of Figure 1, and with the same results.

The ball will always start'its continuous clutching action when a given torque is attained between the members II .and 1, and a variation of the resisting ability of the annular member 5I will of course change the torque value at which the said operation starts.

The balls I6-A and I 6-B of Figure 8 constitute means for effecting unidirectional clutching action of the clutch rollers I9 and 2t. The balls I6-A and I 6-B also effect unidirectional control so that the rollers I9 and 26 will be controlled by the position of the shiftable member 33 to become unidirectional clutch rollers and 'thereby provide selective free-wheeling action vfor direct and intermediate speeds.

In normal forward drive operation the control member 33 in its movement to the left from neutral position depresses the ball -I6-A and thereby the ball I6--B to ride in the cammed tracks 38 and 61 of the member 21, or similar cammed tracks formed in the said member.

With the member II rotating faster than the roller control member -21 in a clockwise direction as indicated by the upper arrow, and with the ball I6-A depressed the ball IG-B is actuated to be moved by the member 21 so as to tend to take its place under theball IB-A and thereby clutch the members I I and 21 to clutch the members II and 1, and to also connect the members II and 1 as hereinbefore described.

As the member 6 and therefore the cammed 'member 21 tends to rotate faster in the samev clockwise direction than the member II the ball I6-B will be moved by the tracks 38 and 41 of the member 21 to the position shown by Figure 8 and no clutching, or free-wheeling action will exist between the members II and 1 or I0 and 1 as a function of the axial position or movement of the slidable member 33. If the member 21 rotates counter clock-Wise' faster than the member I I as indicated by the lower arrow the ball I6-B will be moved under the ball I6--A and thereby clutch the members II and 21 tocause one to drive the other.

With a second set of control balls I1-A and I'I--B (not shown) placed in the. path of the slidable member 33, free-Wheeling action may be obtained for intermediate speed. In normal operation, it is assumed that free-wheeling action will only be desired for direct drive conditions.

While -I have shown and described and have pointed out in the annexed claims-'certain new and novel features o f/myninvention, it will `be understoodthat certain well known equivalents of the elements illustrated may be used, and that various other substitutions, omissions and changes in the form and details of thel device illustrated may be made by those skilled in the art without departing from the spirit of the invention which is indicated in the following claims.

Having thus described my invention, i claim:-

`1. A device for resiliently and positively connecting driving and driven clutch members according to the extent and direction of the torque relations of same, comprising associated reversible unidirectional clutches each with an intermediate fully released position, resilient bidirectional camming means for normally restraining said clutches in said fully released position, said camming means energized by power derived from relative motion of the said members fior moving the clutches into and out of the restrained position, means for deriving the said power from one of the driving members and the driven member and means Afor selectively controlling the power deriving means and therewith the moving action of the said camming means.

2. In a device of the class described, the combination with driving and driven clutch members, said driven member having a plurality of cammed surfaces, clutch rollers cci-operating clutches each with an intermediate fully released position, means in the path of the rollers to normally prevent the clutching action thereof, re-

silient torque actuated camming means associated with the members and preventing means for positively-moving said-clutch rollers and. clutch` members into and' out of a clutching position, and lmeans for edecting said association and thereby selectively controlling the torque actuated means.

3. In a device including driving and driven clutch elements, movable clutchroller means for connecting and disconnecting the said elements, camming means including give-away stop elements actuated by certain relative rotation ci' the driving and driven elements thereby to positively move the clutch rollers to and. trom the said connecting and disconnecting positions, and a selector to control the give-awayA stop elements and thereby the camming means'.

d. In a device oi the class described, the combination. ofw a plurality of axially fixed driving elements each formed with a cylindrical clutching surface and an axially fixed driven element formed with a'plurality of clutching surfaces, a

plurality of reversible unidirectional clutch rollers' designed to be positively moved to eifect a plurality of speed driving relations between said driving elements and the driven element and. to disconnect the said driving relations, clutch roller control means designed to be actuated by power derived from the relative rotation of one of the driving elements and the driven element, means for initiating the power derivation including giveaway stop elements for delaying the actuation of the roller control means, shiftable control'means .for selectively actuating the delaying means, and

a common control means for selectively operating 'the shiftable means.

45. The combination.of a power transmission including a pair of axially xed power members,

one of said power members including a plurality ofY speed driving elements each provided with a clutch portions each with an intermediate fully released position supported by the driven element and adapted to be positively moved in two directions frorn a normally restrained position to establish a plurality of' drive relations between said members, and in two directions from operative positions to prevent driving relations, said clutch moving portions including camming means actuated by power derived from the relative rotation of the power members, control means for causing the camming means to inaugurate the power derivation from the said power members, and a common selector for the camming control means.

6. A clutch device for connecting either of a pair of driving members each provided with a clutching surface with a driven member provided with a pjlurality or clutching surfaces, comprising reversible bidirectional clutch rollers formed for co-cperative association therewith, bidirectional clutch actuating resilient camming means energized by power derived from the relative rotation of certain of the members, means for deriving the said power, means for effecting the said derivation, shiftable means for selectively controlling the effecting means, and a selector for moving the shiftable means.

7. A device for associating driving and driven clutch members in a plurality of drive relations, comprising clutch rollers arranged for clutching association therewith, bidirectional resilient camming means actuated by power derived from one of the driving members andthe driven member .for positively controlling the clutchrollers from,

surface and. a driven i member provided with a plurality of clutching surfaces, a plurality vof sets of clutch rollers positioned for co-operative association therewith, power actuated camming means for bidirectionally moving selected rollers as a function of' the torque relations of one of the driving members and the driven member, means for intermittently deriving the said power from the selected member means for initiating the operation of the intermittent means, and a selector for selectively controlling the initiating means.

9. )In a device of the class described, means including two driving clutch members and a driven clutch member, a plurality of clutch rollers cooperatively associated with the said members, 'pov/'er actuated means for controlling the said cci-operative association, said power actuated means including a plurality of bidirectional cam sets and a common resilient element positioned therebetween to absorb power therefrom and to return said power thereto, means for associating one of the elements of one of the cam sets with one of the driving members and the other element of the cam set to the driven member. to obtain the said power therefrom, means for causing the said association, and a selector for selectively controlling the causing means.

10. A clutch device for coupling either of a pair of driving members each formed with a clutching portion with a driven member formed with a plurality of clutching portions, comprising clutch rollers arranged for clutching engagement therewith, interlocked reversible unidirectional torque actuated camming means for positively effecting the said engagement, means for obtaining the said 'torque from one of the driving members and the driven member, axially movable means for permitting the torque obtaining action, and a control for the movable means.

11. 'A device for placing driving clutch members and a driven clutch member into and out of a plurality of speed drive relations, constituting gripping members in the form of rollers carried by the driven member for co-operative association therewith, means including bidirectional cam sets and a common associated resilient element energized by power taken from one of the driving members and the driven member for positively moving and holding the said rollers, means for causing the bidirectional means to take the said power from the said members, means for initiating and maintaining thev causing action, and means for controlling the causing action selectively through the operation of the initiating means, said resilient element designed to exchange power with the cam sets as a function of the torque relations of one of the driving members and the drivenmember.

12. A clutch device for positively connecting and disconnecting driving members each including a clutch surface and a driven member includlng a plurality of clutch surfaces, including clutch rollers positioned between the said members for clutching association therewith, means including cam sets each including an element positioned on the driven member for rotation therewith and an element for moving the clutch rollers, said cam sets actuated by power taken from one of the driving members and the driven member, a power absorbing and exchanging element positioned for common association with the said cam sets, means for obtaining the said power for the said cam sets and said power element from the said members,

and means for selectively controlling the saidpower obtaining action, said power element receiving power from the cam sets and delivering power to the same as a function of the torque ,relations of the said driving members and the driven member.

13. A device for resiliently and `positively coupling and uncoupling driving clutch elements: and

a driven clutch element as a function of the torque 14. A device for initially connecting driving clutch members and a driven clutch element into a plurality -of resilient speed drive relations andh to permit each resilient speed relation to become a positive drive relation during intervals of excessive driving torque, interlocked -resilient power actuated camming means for eiecting said speed relations according to the torquev relations of one of the driving members and the driven member, slip-clutch means for obtaining the actuating power from the said selected members, and means for controlling the power obtaining means.

15. In a device of the character described, the combination with driving and driven clutch members, interlocked torque actuated camming means for resiliently connecting either of the driving members with the driven member, saidactuating torque automatically obtained from one of the driving members and the driven member and stored and returned to same as a function of the torque relations of same, and means for 'controlling said torque obtaining action.

16. A device for connecting driving Vmembers each with a clutching surface and a driven mem` ber with a plurality of clutching surfaces, gripping members in the form of rollers co-operating therewith to act as clutches, resiliently associated interlocked bidirectional camming means actuated by virtue of the relative rotation of either of the driving members and the driven member for causing the gripping members to connect said driving member and the driven member and thereafter to disconnect the members due to power stored during the connecting period, and means for permitting the relative movement of either of the driving members and the driven member to cause the said actuation and the said storage of power.

17. In a roller clutch type transmission including driving and driven clutch members and relatively movable roller clutch elements therebetween for co-operative association therewith, a plurality of resiliently associated interlocked cam sets actuated by power received from one of the driving members for moving the clutch rollers according to the torque of the said driving member, means for obtaining the actuating power from the said driving member, and a control means for said power obtaining means, one element of each of the cam sets positioned on the driven member for rotation therewith and the other element of eachA cam set loosely mounted on the said driven member.

18. A device for resiliently and positively connecting a driving member and a driven member each forming a portion of a clutch organization, including clutch rollers for co-operative clutching association therewith, power actuated means for continuously controlling the said association,v

resilient camming means for continuously deriving, storing and returning the said power during a given connection as a function of the relative rotation of the members, means for selectively controlling the power deriving means, and means for moving the selectively controlled means.

19. In a device of the class described, the combination of a plurality of axially xed driving .elements each formed with a cylindrical clutching surface and an axially ixed driven element formed with a plurality of clutching surfaces, a plurality of clutch rollers designed to be moved in two directions from a normally restrained position to co-operate with said elements, means including power actuated interlockedcam sets and a compressible member for mom'ng certain of the said rollers as other rollersare restrained, means for obtaining the actuating power from one of the driving elements and the driven ele ment, and a common control means designed to Y member clutch Yroller means for selectively causingthe said members to assume the said drive relations -when moved relative thereto, torque actuated means for receiving power from one of the driving members and the driven member for moving the said rollers according to the torque relations of the. said members; means for deriving the said power from the said driving member and the said driven member, movable means for controlling the said power deriving means whereby the torque actuated means will selectively hold or move the rollers to a resilient speed drive relation and thence to a positive speed drive relation.

21. In a device of the class described, the combination of a plurality of axially fixed driving elements each formed with a cylindrical clutching surface and an axially xed driven element formed with a plurality of clutching surfaces, a plurality of clutch rollers designed to be moved in two directions from a normally restrained position toco-operate with the said elements, means including power actuated interlocked cam sets for ,positivelyv moving certain of the said rollers into a clutching position, said power actuated means including power absorbing means arranged to become actuated to positively move the certain said rollers out of a clutching position, means for obtaining the said actuating power from one of the driving members and the driven member, a common control means for selectively controlling the power obtaining means according to the extent and direction of its movement along a given path, and a selector for moving thev common control means.

22. A clutch device for connecting either of a pair of driving clutch members with a driven clutch member, including a plurality of gripping members co-operating therewith to eect a plurality of Vspeed driving relations, means actuated by power derived from one of the drivingy clutch the power obtaining means, and aselector for moving the control member.

23. A clutch device for 'positively connectingV and disconnecting driving members each provided with a clutching surface and a driven member provided with a plurality of clutching surfaces, including reversible unidirectional gripping members with an intermediate fully released position co-operating therewith to act as clutches, torque controlled camming means for positively moving said gripping member into a clutching position, power actuated means cci-operatively associated with the said camming means for positivelymoving the said grlpping'members out of a clutching position, means carried by the said driven mem-- ber for obtaining said torquer and thereby said actuating power from a selected driving-member and said driven member, movable means for selectively controllingthe power obtaining means, and an axially movable selector for moving the movable means.

24. Ina device of the class described, the combination of two driving clutch members and a driven clutch member, rollers acting therewith to act as clutches, power actuated means for bidirvrrectionally moving the rollers, means for taking ing means including cam sets each provided with a clutching surface and mating cam surfaces, a power absorbing member positioned between the cam sets for exchanging power therewith, a slidable member formed with two cam clutching surfaces, gripping members positioned between-the cam vsets and the slidable member and rotatable with the driving members, and a selector for moving the slidable member to and from a clutching engagement with the gripping members.

25. A clutch device for associating driving members and a driven member in a resilient drive relation, comprising normally restrained camming means co-operatively associated therewith, power actuated means for removing said restraint and thence actuating said cams as a function of the torque relations of one of the driving members and the driven member, overmember and associated clutch elements positioned between the driving and driven members, power actuated interlocked camming means including a power absorbing and exchanging element arranged to become active as a function of the torque relations of one of the driving members and the driven member, and over-running clutch lmeans associated with one of the driving members and the camming means for obtaining the actuating power from the said driving member and the driven member, means for initiating and maintaining the said obtaining action thereby to eiect the said association, and means for controlling the initiating means.

27. In a multi-speed clutch organization including a plurality of driving members with clutching portions, a driven member with a plurality of clutching portions, and a plurality of sets of' associated clutch rollers, intermittent over-running clutch power actuated camming means including a power aetuated spring positioned between said camming means, said spring arranged relative tothe said camming means so as to become a power exchanging device as a function of the torque relations of one of the driving members and the driven member, and clutching means carried by the camming means and positioned by the said driving members, said clutching means controlled by a shiftable member carried by the driven member and rotatable therewith to obtain the said actuating power.

28. In a multi-speed roller clutch organizationV .thereafter vdisassociating a. 'driving member and the driven member, over-running clutch means for obtaining the said actuating power, and a control for the said obtaining means.

29. A clutch device for resiliently connecting either of a pair of driving members with a driven member, including a power actuated camming set positioned between each driving member and the ydriven member, a plurality of sets of gripping members, each gripping set zzo-operatively associated with a cam set, a driving member and the driven member, means constituting a shftable member for selectively causing the gripping members to assume a gripping position between a selected cam set, a driving member and the shiftable member to derive the actuating power. for

the cam set, a common power exchanging element positioned between the cam sets for selective exchange of said power, said power exchange occurring as a function of the torque relations v of the said driving member and the driven member, and means for moving the shiftable member relative to the driven member as it rotates therewith.

30. A multi-speed resilient-positive drive power transmission device including a plurality 'of driving members and a driven member concentrically arranged, a plurality Voi symmetrically disposed member carried by the driven member and positioned between said cam sets to selectively exchange power therewith as .a function oi? the torque relations of one of the driving members and the driven member, means for moving the slidable member, and means for co-operatively associating a cam element, a driven member and the slidabie member to obtain power from the said driving member and the driven member.

HWARD J. MURRAY. 2o 

